Spinner device for turning well pipe or the like



J. BARTOS 3,461,974

SPINNER DEVICE- FOR TURNING WELL PIPE OR THE LIKE I 'Aug. .19, 1969 4' Sheebs-shee t l Filed June 26 1967 J. BARTOS SPINNER DEVICE FOR 'ruaumo WELL PIPE on THE LIKE Aug. 19, 1969 4 Sheets-Sheet 2 Filed-June 26. 1967 I.\VENTOR. Jose/=- .Bnreros m: m: a:

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Kug.'1",'1 9 6'9" J. laAFmns i "3,461,974' I Q I SPINNER DEVICE FOR-TURNING WELL PIPE on THE LIKE rim June 26 1967 .4 Sheets-Sheet;

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3,461,974 SPINNER DEVICE FOR TURNING WELL PIPE OR THE LIKE Josef Bartos, La Puente, Calif., .assignor to. Abegg and Reinhold, Los I Angeles, Calif., a corporation of California Filed June 26, 1967, Ser. No. 648,913 Int. Cl. E21b 3/02; E21c 7/10; F04c 1/02 US. Cl. 173-3 24 Claims ABSTRACT OF THE DISCLOSURE A spinner for turning a section of well pipe and including a vane type motor disposed about a tubular pipe sub which is connected to the upper end of the well pipe, and having a clutch adapted to break the coupling between the motor and the pipe sub in response to the development of pressure in the drilling fluid within the well string, to thereby prevent damage to the motor or other apparatus by turning of the string during drilling.

Cross references to related applications Certain features of the apparatus of the present invention have been disclosed and claimed in my prior copending applications Ser. No. 453,954, filed May 7, 1965, on Well Pipe Spinner, and Ser. No. 454,055, filed May 7, 1965 now Patent No. 3,381,584 on Vane Type Rotary Devices.

Background of the invention This invention relates to spinner devices for turning a section of well pipe, usually including a kelly, for the purpose of rapidly making or breaking a joint. The spinner is desirably connected into the upper end of the well string, between the kelly and the swivel, and may include a tubular body element throughwhich drilling fluid passes from the swivel into the string during. a drilling operation.

A spinner of this type is often left in the string even when not in use, and while the string is being driven rotatively by the usual rotary table. However, ifv the.

Summary of the invention The present invention is concerned primarily with the provision of means for positively preventing damage or injury of the above discussed type, by assuring that the spinner will be in an inactive condition in which it cannot drive the drill string during an actual drilling period. Wheneverthe drilling is stopped, however, and the operator prepares to utilize the spinner for a joint making or breaking operation, the spinner automatically converts to an active condition in which it is then fully capable of turning the Well pipe.

This result is accomplished by the provision of automatic control means which are responsive to changes in the pressure of thedrilling fluid which circulates through the swivel, spinner, and drill string downwardly into the well. In conventional drilling operations, the pressure of this fluid is invariably reduced, to stop the flow of the drilling fluid through the. string, whenever it is desired to utilize the spinner; for making or breaking a joint.

The present apparatus responds to this reduction in pressure -to actuate the spinner to a condition in which it cannot drive the drill string, desirably by actuation of a clutch to breakthe coupling between the spinner motor and the pipe. The automatic control may be subjected to the drilling fluid pressure through an opening in the wall of the tubular sub which carries the rest of the spinner structure.

In accordance with the teachings of my above mentioned prior application Ser. No. 454,055, the motor of the spinner is preferably a vane type motor disposed about a tubular sub. Certain additional features of the present invention relate to improvements in this vane type motor, relating to the manner in which pressure fluid is admitted to and discharged from the motor, and relating to the actuation of the vanes themselves.

Brief description of the drawings The above and other features and objects of the invention will be better understood from the following detailed description of the typical embodiments illustrated in the accompanying drawings, in which:

FIG. 1 is a somewhat diagrammatic side view of a drill rig having a spinner constructed in accordance with the invention;

FIG. 2 is an enlarged fragmentary representation of a portion of FIG. 1;

FIG. 3 is a further enlarged view taken on line 33 of FIG. 2;

FIG. 4 is an enlarged view taken primarily on the vertical sectional line designated 4-4 in FIG. 3;

FIG. 4a is a fragmentary representation of one of the valve units of FIG. 4, in a changed position;

FIG. 5 is a horizontal section taken on line 55 of FIG. 4;

FIGS. 5a and 5b are fragmentary vertical sections taken on lines 5a5a and 5b5b respectively of FIG. 5

FIG. 50 is an enlarged horizontal section through one of the vanes of the device;

FIG. 6 is a fragmentary view representing a portion of FIG. 5, but with the clutch in its released condition;

FIG. 7 is a fragmentary vertical section taken primarily on line 7--7 of FIG. 6;

FIG. 8 is a fragmentary elevation, partially broken away in section, taken on line 8-8 of FIG. 7;

FIG. 9 is a view similar to FIG. 7, but showing a variational form of the invention;'

FIG. 10 shows a portion of FIG. 9 in a position in which the clutch is released; and

FIG. 11 is a fragmentary horizontal section taken on line 1l11 of FIG. 9.

Description of the preferred embodiments Attention is first directed toFIG; 1, in which there is shown a conventional well drilling rig 10 having a rotary table 11 which turns about a vertical axis 12, and is adapted to drive rotatively about that axis the usual noncircular 'kellyf section 13 of the drill pipe. The rest of the drill string is of course connected to the kelly and extends downwardly into the well. The entire drill string is suspended by the usual elevator assembly designated 14 in FIG. 1, which includes a block and tackle assembly 14' driven by a motor 15,- with the cable 16 of the block and tackle carrying a hook 17. 'The swivel is illustrated at 18, and has an upwardly projecting bail 19, which engages-and is suspended by hook 17 of the elevator assembly. The swivel of'course includes an outer The circulating fluid is pressurized by a pump represented at 24, which is in operation during rotation of the well string to produce circulation of drilling fluid downwardly therethrough, but which is stopped whenever a joint in the string is to be made or broken.

The spindle 21 of the swivel projects downwardly a short distance beneath the lower end of the non-rotating body 20, and has external threads 25 connectible to a spinner 26 with whose construction the present invention is primarily concerned. This spinner includes a vertically extending short pipe section 27 (see FIGS. 2 and 4), containing a passage 28 through which drilling fluid passes downwardly from swivel stem 21 to the kelly. The upper end of pipe section 27 is internally threaded at 29, to form a box end into which the threads 25 of the swivel stem or spindle are connectible. Alternatively, there may be connected between the swivel stem and section 27 of the spinner an intermediate short pipe section or sub. The lower end of pipe section 27 may have an externally threaded downwardly projecting end 30 which may be connected to the kelly through a conventional kelly cock section 31 having a kelly cock valve 32 for closing off the flow of fluid through the string when necessary. The kelly cock section in turn is connected to the upper end of the kelly 13 by an appropriate threaded connection, with section 31 of course containing a passage forming a continuation of the passage 28 in pipe section 27 of the spinner, so that fluid may flow downwardly through section 31 to the kelly and into the well. The joint between sections 27 and 31 as well as the joint between section 31 and the kelly, may be locked against accidental detachment by appropriate external locking rings 33 and 34 suitably connected to the joined parts.

In addition to the central tubular pipe section 27 of the spinner, this device includes and forms, about section 27, a vane type fluid driven motor 35, including an outer non-rotating housing or body 36, and a rotor 37 which in one condition of the apparatus acts to drive pipe section 27 and the connected parts rotatively about vertical axis 12. The rotor is capable of driving the well pipe in either rotary direction, and for this purpose two flexible fluid inlet hoses 38 and 39 may be provided, to lead actuating pressure fluid, typically compressed air, into housing 36, for driving the rotor in its opposite directions. The fluid may be delivered to hoses 38 and 39 from a source 40 of compressed air or other pressurized fluid, through a three-way valve 41, which is actuable to three positions, for admitting air selectively to either of the two hoses, or closing off all air to both hoses.

Housing 36 contains and forms an inner annular chamber 42 (FIGS. 4 and 5) within which rotor 37 is mounted to turn. The housing may be formed sectionally of several parts, including a generally annular main section 43, a generally annular top wall or section 44, and a series of radially outer cover plates 46. At a series of evenly circularly spaced locations (desirably five such locations),

the sections 43 and 44 have radially outwardly projecting portions or enlargements forming outwardly projecting portions 47 of the housing, within which a series of radially movable vanes 48 are slidably received. Sections 43 and 44 are secured rigidly together in any suitable manner, as by several sets of screws 49 extending downwardly through top section 44 and into bottom section 43 at the locations of the outwardly projecting enlargements 47, and by several similar screws 50 extending through section 44 and into section 43 at a number of circularly intermediate locations (FIG. 3). Outer cover plates 46 extend across the radially outer extremities of sections 43 and 44 at the locations of outwardly projecting portions 47, and are secured thereto by bolts 51.

The previously mentioned rotor chamber 42 in the housing is defined at its top and bottom by two annular parallel horizontal surfaces 52 and 53, formed on the underside of section 44 and the upper side of section 43 respectively, and both disposed perpendicular to axis 12.

The radially outer extremity of chamber 42 is defined by a generally annular wall 45 projecting upwardly from and desirably integral with section 43 of the housing, and having an inner cylindrical wall surface 54 centered about axis 12 and extending vertically from surface 52 to surface 53. Wall 45 is circularly continuous except at the locations of outwardly projecting enlargements 47 on the housing, at which locations wall 45 is interrupted to provide radially extending slots or guideways 247 within which vanes 48 and their guiding parts are received.

Vanes 48 are rectangular flat elements of a height corresponding to the vertical distance between the two top and bottom wall surfaces 52 and 53 of chamber 42, to be slidably received therebetween. More specifically, as seen in FIG. 4, one of the vanes is there illustratedas having a bottom horizontal edge 55 slidably engaging surface 53 of housing section 43, and a top horizontal edge 56 slidably engaging surface 52 of top section 44. The radially outer extremity of the vane may be defined by a vertical edge 57, while the radially inner extremity of the vane may be defined by a vertical edge 58, desirably containing a vertical groove 59 (see FIGS. 4 and 5) within which there is retained by rivets or screws 259 a seal element 60 formed of nylon or other sealing material and extending vertically between surfaces 52 and 53. The vane 48 may be formed of any suitable preferably rigid material, such as an appropriate metal, and may be slidably confined between two bearing carrier plates 60 and 61 (FIG. 5), confined within one of the housing slots 247. Plates 60 and 61 may be formed of an appropriate metal, such as steel, and be welded to section 43 or otherwise permanently secured in the illustrated positions. Plates 60 and 61 have parallel opposed vertical planar surfaces 260 and 261, extending substantially radially with respect to axis 12, and containing vertical grooves within which there are loosely received vertical bearing inserts 62 of an appropriate bearing material (such as nylon or aluminum bronze) for minimizing the frictional resistance to motion of the vanes. The two elements 60"and 61,

and their inserts 62, form together the opposed vertical side walls of a guideway within which the vane 48 is mounted for sliding movement directly radially with respect to the main axis 12 of the spinner.

Each of the vanes is spring urged radially inwardly against the rotor by a coil spring 64, which may be received about a pin 65 projecting radically inwardly from the associated cover plate 46, with the spring projecting into a suitable passage 66 in the vane (FIGS. 4 and 5), and bearing against a shoulder at the end of that passage. The radially outer end of the vane receiving guideway may be sealed by provision of an appropriate seal between each of the cover plates 46 and the other housing parts (sections 43 and 44), peripherally about the vane area, and more specifically by providing an endless typically rectangular gasket 67 (FIGS. 4 and 5) for preventing leakage of air from the housing. The radially inner extremities of the two bearing carrier plates 60' and 61, at each of the vane locations, may have arcuate surfaces which form continuations of the cylindrical surface 54 of housing wall 45.

The opposite side surfaces 68 of each of the vanes are parallel to one another, and extend vertically, but are spaced apart a distance somewhat less than the space between the opposed parallel planar vertical surfaces 263 of each pair of bearing elements 62, to provide a clearance space between each of the vanes and one of the surfaces 263 (as at 363 in FIG. 50) through which some of the air from within chamber 42 may flow radially outwardly to a location outwardly beyond the vane.'This air always flows radially outwardly at the pressure side of the vane, while the latter is maintained by the pressure in sealing engagement with the bearing surfaces 263 at its opposite side (as at 463 in FIG. 50).

The entire housing 36 is mounted rotatably to the central tubular main pipe section portion 27 of the spinner, since pipe section 27 is to turn with the rest of the drill string while the housing remains stationary. For this purpose, there are provided two bearings 69 and 70 about pipe section 27, and-at the upper and lower ends of the housing. Each of these hearings may have inner and outer races with rollers 71 received therebetween, and disposed at inclinations enabling bearings 69 and 70 to function as thrust bearings, so that in addition to mounting section 27 for rotation within the housing, they also retain the housing against both upward and downward movement relative to pipe section 27, and in fact serve to support the weight of the housing and its contained rotor from pipe section 27. The inner race of bearing 70 may engage against and be supported by an upwardly facing annular shoulder 72 formed on pipe section 27, while the inner race of bearing 69 is retained against upward movement by a snap ring 73 received within a groove in pipe section 27, and acting against bearing 69 through a washer 74.

Roller bearing 69 may be protected against contamination by a shield ring 75 disposed about pipe section 27 and secured thereto by set; screws 76, with this shield ring coacting with another ring 77 of the configuration illustratedin FIG. 4, secured to upper wall 44 of the housing by bolts 78, and containing an annulardeformable seal element 79 engaging a depending skirt on ring 75. Th lower roller bearing 70 may be protected by connection of a shield ring 80 to' the housing through screws 81, with ring 80 containing seal elcments82 engageable with an annular surface 83 on pipe section 27. I

The rotor 37 is mounted rotatablywithin chamber 42 by means of two ball bearings 84 and 85 (FIG. 4), whose outer races engage and are confined by housing sections 43 and 44 respectively. The rotor itself has surfaces 86 which define the inner races of thes'e'ball bearings, with the ball contacting surfaces all being disposed at such an angle as to give the bearings a capacity to function as thrust bearings, in addition to 'merely mounting the rotor for turning movement. The rotation of the rotor is of course about main axis- 12 of the apparatus.

The radially outer portion 237 of the rotor occupies the entire vertical distance from bottom wall surface 53 of chamber 42 to top wall surface 52 of the'chamber, and has a radially outer surface 87 which is circularly continuous about axis 12, and which has the non-circular horizontal cross sectional configuration illustrated in FIG. 5. This cross section continues for the entire vertical extent of chamber 42, to define a series of evenly circularly spaced radially outwardly projecting lobes 88 on the rotor, and circularly intermediate portions 89 of surface 87 which, in advancing circularly from one of the lobes to the next lobe, first progressively decrease in radius, and then progressively increase in radius to the next lobe. The lobes 88 are of a diameter corresponding substantially to the diameter of internal surface 54 of the housing, to engage or substantially engage that surface continuously, and move therealong, so that there are formed between successive lobes, a series of air compartments 90, forming portions of chamber 42 which are isolated from one another. These compartments in effect vary progressively in size as the rotor turns, since vanes 48 also form sides of the compartments. As the rotor turns, the vanes of course move inwardly and outwardly, to always contact the outer surface 87 of the roller in sealed relation.

The radially inner portion of rotor 37 contains two annular fluid inlet and fluid outlet passages 91 and 92, which have the vertical cross sectional shape illustrated in the left hand portion of FIG. 4 except at the locations of certain later-to-be-described openings by which these passages communicate with the exterior of the rotor. More specifically, the'upper passage 91 opens upwardly,.'while the lower passage 92 opens downwardly. Annular sealv elements 93 and 94 may be contained within annular grooves in the housing to annularly engage the upper and lower surfaces of the rotor radially between passages 91 and 92 and the outer compartments 90', to thus form-a sealtherebetween. Also, the bearings 84 and 85 may be sealed by annular seal rings 95 and 96 (FIG. 4) to prevent escape of any of the air from passages 91 and 92 into or through the bearings.

As seen in FIGS. 5 and 5a, the upper fluid inlet and outlet passage 91 in the rotor communicates with compartments 90 through a series of openings 97 extending radially through the outer wall of the rotor at first sides of the lobes 88. Similarly, lower passage 92 communicates with compartments 90 through a series of openings 98 (.See broken lines in FIG. 5 and see showing of FIG. 5b), at the opposite sides of lobes 88.

The first air inlet hose 38 communicates with the upper interior portion of the housing through a fitting 99 (FIG.

4), which opens into a cylindrical radially extending passage 100 in upper wall 44 of the housing, the opposite end of which passage communicates downwardly at 101 with the discussed upper passage 91 in the rotor.

Passage 100 in the upper portion of the housing also communicates with the atmosphere through a vent outlet 103, past a shield cap 104, with vent outlet 103 opening into the side of the cylindrical passage 100. A slide valve element 105 is slidably mounted within passage 100 for movement between the positions of FIGS. 4 and 4a. In. the position of FIG. 4a, the tubular side wall 106 of the slide valve element extends across and closes vent outlet opening 103, to prevent the loss of any air from passage 100 to the atmosphere.

Element 105, in addition to serving as a slide valve element, also functions as a portion of a shiftable two valve assembly, and for this purpose contains a second valve element 107, adapted to seal annularly against a valve seat surface 108 formed at the end of the tubular side wall 106 of the slide valve element. The second valve element 107 has a stem 109 which is slidably guided to mount element 107 for only axial movement, and about which there is received a coil spring yieldingly urging element. 107 to its closed position of FIG. 4. Stem 109fprojects leftwardly beyond the end of slide valve element 105, for engagement with a transverse surface or shoulder 111 in the housing, in a manner automatically shifting the second valve element 107 to its opened position'of FIG. 4a in response to leftward movement of element 105 under the influence of compressed air admitted through fitting 99. Spring is of a strength or force enabling such compression of the spring, for opening of valve element 107, in response to the application of air pressure to the slide valve element 105.

The second air inlet line 39 communicates through a fitting 99a with a passage 100a corresponding to upper passage 100, and containing a second slide valve element 105a corresponding to upper valve 105 and containing a spring pressed valve corresponding to valve 107. This lower valve assembly is constructed and functions in the same manner as the upper valve assembly to control the flow of air between inlet line 39, a vent outlet opening 103a, and a passage 101a leading into passage 92 in the rotor.

The outer housing 36 of the spinner and its motor is retained against rotation about axis 12* by connection to the upper bail 19 of swivel 18 through a flexible vertically extendingcable 112. The lower end of this cable may be connected to the housing by forming One of the outer cover plates 46 of the housing to have an integral radially outwardly projecting partial spherical socket portion 113 (FIGS. 3 and 4), within which there is received a mating part 114 having a spherically curved ball portion 115 forming a universal connection with socket 113. The lower end of the cable may have an eye portion 116 forming an A opening through which a connector pin 117 extends, with that connector also extending through openings in a pair 0f upwardly projecting ears 118 on a part 119, which has a partialspherical portion 120 engaging the upper surface of socket 113, and a downwardly projecting shank 121 to which a nut 122 is connected A spring 123 bears down- Wardly against an element 124 retained by the nut, and upwardly against part 114, to yieldingly retain the parts in their FIG. 4 relative positions, while allowing limited resilient upward movement of the lower end of the cable relative to the housing in response to excessive forces. The upper end of the cable is connected to the bail by means of a connector bracket 125, detachably secured in any suitable manner to bail 19, as by a clamp structure represented at 126 and extending about a portion of the bail, with bracket 125 projecting outwardly far enough for connection to the cable at a loction 127 positioned so that the cable may extend directly vertically past the main body of the swivel. As will be apparent, the cable 112 does not support the weight of housing 36 or the rest of the spinner structure, but rather merely retains the housing against rotation about axis 12, while at the same time allowing some limited rotary motion ofthe housing about that axis in response to excessivetorsional forces, to thus introduce a certain amount of resiliency into the structure for holding the housing against rotation. The actual support of the weight of the housing and other parts of the spinner is effected through the central pipe section 27 and the various bearings which mount the spinner on that section, as has been previously indicated.

When the spinner is in use, rotor 37 is connected in driving relation to pipe section 27 by means of a clutch mechanism represented generally at 128 in FIG. 4. This mechanism includes two diametrically opposite clutch levers or elements 129, which are movably carried by a ring or sleeve 130 disposed about and rigidly connected to pipe section 27. Internally, this ring 130 is a close fit on the outer surface of pipe section 27, and is keyed thereto for rotation with the pipe section by a key represented at 131 in FIG. 5. The levers are mounted pivotally to ring 130 within two vertically elongated slots 132 in the ring, and by a pair of horizontal pivot pins 133 extending through the keys and into the material of the ring. Beneath the level of pivot pin 133, each lever 129 has a downwardly projecting arm portion 134, which is engaged by a pressure actuated piston or plunger element 135 mounted for movement directly radially of axis 12, and along a radial axis 136, relative to pipe section 27. This piston 135 may be slidably mounted within a cylinder sleeve 137 which is a pressed fit within a cylindrical opening 138 extending through the side wall of pipe section 27. To seal piston 135 with respect to cylinder 137, the radially inner end of the piston may carry an externally cylindrical seal element 139 of rubber or other resilient material, which is a tight slightly compressed fit within the sleeve, and which desirably projects slightly inwardly beyond the wall or passage 28 in the FIG.-4 position of the clutch. Seal element 139 may be secured to piston 135 by molding it about a head or projection 140 formed onthe piston. As will be apparent, when pressure is applied to the radially inner end of the seal portion 139 of the piston, by drilling fluid or mu within passage 28, the piston is actuated by that pressure radially outwardly from the FIG. 4 position to the FIG. 7 position, to thereby swing lever 129 to its FIG. 7 position.

Upwardly above the level of pivot pin 133, each of the clutch levers 128 has an upwardly projecting arm portion 141, which may be offset slightly radially inwardly and be received partially within a vertically extending groove or recess 142 in the outer surface of pipe section 27, and which is yieldingly urged radially outwardly by a coil spring 143 to normally retain the lever in its FIG. 4 position. The upper end of arm 141 forms a radially outwardly projecting clutch lug 144, which is enlugs 145 lie within planes which extend substantially radially and axially with respect to axis 12. In the FIG. 7 position of each of the clutch levers 129, these levers are moved out of driving engagement with rotor lugs 145, so that pipe section 27 may turn freel without corresponding rotation of the rotor. A seal may be provided annularly between the upper end of ring and the upper portion of the housing, at a location beneath bearing 71,'by a seal element 148 (FIG. 4).

To now describe the operation of the apparatus of FIGS. 1 through 8, assume that the spinner 26 is connected into the drilling apparatus at the location illustrated in FIGS. 1 and 2, beneath swivel 18, and thatthe rigis initially being utilized in an actual drilling operation, with the kelly section 13 of the pipe string being driven rotatively by rotary table 11, to thus drive the rest of the string and the drill bit for deepening the well. During such rotation of the string by the rotary table, drilling fluid or mud is supplied to the swivel through line 22 of FIG. 2, and flows downwardly under pressure through the stem 21 of the swivel, and through pipe section 27 of spinner 26, to then enter and flow downwardly through the kelly and into the lower portion of the string. The pressure of this drilling fluid acts against the seal portion 139 of piston in FIG. 4, to force that piston radially outwardly from its- FIG. 4 position to its FIG. 7 position, and thus pivot the clutch lever 129 to its FIG. 7 position in which it does not transmit rotary motion between pipe section 27 and the rotor 37 of the spinner. Thus; pipe section 27 of the spinner is free to turn with the stem of the swivel and with the kelly and the remainder of the well string, without turning motion of the rotor or any other portion of the spinner. Such disconnection of the spinner or rotor from the turning parts prevents damage to the rotor by unnecessary turning, and

also prevents any possibility of the string being retained against rotation by binding of the rotor 37 within the spinner housing, such as might occur for example if particles of dirt or other foreign materials were in some Way to lock the rotor or its bearings against rotation. This binding is not a major factor, but could be so disastrous to all of the equipment in the vicinity, and even to persons working in the area, as to render it desirable to take every precaution against the possibility.

When it is desired to utilize the spinner for driving the kelly and pipe string, this will always occur after mud pump 24 has been deenergized, to stop the flow of circulating fluid through the string, and thereby reduce the pressure within passage 28 of pipe section 27 (FIG.

- 4). As soon as the mud pressure is reduced, springs 143 will actuate the two clutching levers 129 to their active FIG. 4 positions, in which they become effective to transmit rotation from rotor 37 to pipe section 27. If it is then desired to turn the pipe section 27 and kelly ,13 in a clockwise direction, selector valve 41 of FIG. 1 is actuated to a position to admit compressed air through'hose 38 to the spinner. This compressed air moves slide valve element 105 from its FIG. 4 position to its FIG. 4a position, to thereby close off communication through outlet 103 to the atmosphere, and with the final portion'of this motion serving to open valve 107 so that the compressed air may enter passage 91 of the rotor, and from that passage discharge through openings 97 in the rotor'into the variable sized compartments formed between the retor and the housing. The compressed air within these compartments drives the rotor in a clockwise direction, as viewed in FIG. 5, since the compartment into whichthe air is admitted will increase in size progressively during such right hand rotation. The vanes 48 engages the rotor in a valving relation, so that until aparticular'one of the openings 97 reaches one of the vanes, that opening admits air to a compartment at a first side of the vane, but after passing the vane the air is admitted to the opposite side of the vane.

While the rotor is turning in a clockwise direction, the openings 98 act as outlet openings, through which the air is forced into passage 92 of the rotor, for discharge through outlet 103a of FIG. 4 to atmosphere. If it is desired to reverse the rotation of the rotor, this may be effected by actuating selector valve 41 to a position in which the air to hose 38 is shut off, and compressed air is admitted instead to hose 39. This air will actuate the lower valve 105a leftwardly to a position corresponding to that shown for the upper valve in FIG. 4a, while the upper valve returns rightwardly to its FIG. 4 position under the influence of air discharging from passage 91 to the atmosphere through outlet 103. That is, the reduced diameter portion 150 of slide valve 105 acts within reduced portion 151 of the passage 10 as a piston, which is forced rightwardly by the discharging air, with thispiston effect being enhanced in the final portion of the travel by confinement of the larger diameter portion of slide valve element 105 within the larger diameter portion of passage 100. During the reverse or counterclockwise rotation, the air which enters bottom annular passage 92 of the rotor flows outwardly into the compartments between the rotor and housing through openings 98, while the discharging air leaves those compartments through openings 97 and passage 91 of the rotor to actuate the upper valve element 105 to open position as previously discussed, and thus discharge to atmosphere.

When drilling is again to be resumed, this will only be done after pump 24 of FIG. 2 has again been energized to produce a flow of drilling fluid and to produce a pressure within passage 28, to thus return the clutch levers 129 to their FIG. 7 inactive or released positions, so that the drill string may then be turned without rotation of rotor 37. Desirably, the clutch elements and their springs 143 are so designed as to be actuable from their FIG. 4 positions to their FIG. 7 positions by a pressure of between about 200 and 500 pounds per square inch within passage 28. The seal element 139 prevents access of any of the drilling fluid to the clutching parts.

During rotation of rotor 37, vanes 48 are continuously held radially inwardly against outer surface 87 of the rotor by the combined action of springs 64 and air pres,- sure'exerted radially inwardly against the vanes. To bring out the manner in which the pressure of the air exerts a radially inward force against the vanes, reference is made to FIG. in which it may be assumed that compressed air at relatively high pressure is contained within the compartment 90a to the right of the vane, while air is being discharged from the compartment 90b to the left of the vane, and is therefore at a reduced pressure in compartment 90b. Because of the greater pressure in compartment 90a, vane 48 of FIG. 50 is urged leftwardly by the air pressure and into tight sealing engagement with the two left hand seal strips 62, as indicated at 463, while a gap is left between the two right hand seal elements and the vane, as indicated at 363. Thus, the high pressure air from compartment 901: can flow radially outwardly through the gaps at 363 and into the space 563, to exert a radially inward force against the vane. This force is partially counteracted by the exertion of a radially outward force against the inner extremity of the vane (toward the bottom of FIG. 50), but because the vane assembly contacts outer surface 87 of the rotor at 248, the outward force against the vane can be exerted against only one half of its inner extremity, that is the portion to the right of contact line 248 but not the portion to the left of that contact line. Thus, there is a net differential pressure tending to urge the vane radially inwardly, and coacting with spring ,64 in assuring that the vane will continuously contact the rotor. When conditions reverse and the pressure in compartment 90b of FIG. 50 exceeds that in compartment 90a, the vane shifts rightwardly to contact the bearing elements at its right, and provide air leakage gaps at the left side of the vane, so that in all conditions the high pressure side of the vane is in communication with the radially outer space 563, to attain the desired result of exerting a net differential force radially inwardly against the vane. It is also noted that each vane may contain a passage 2'00 (FIGS. 4 and 50) through which air may flow through the interior of the vane past the radially outer pair of bearing elements 62, to reduce the resistance to flow of air outwardly past those elements, but with the passage 200 being so located as to never move far enough radially inwardly to bypass the two radially inner bearing elements 62, so that a seal will always be formed with one of these inner elements. The passage 200 may consist of a transverse opening 201 extending entirely through the thickness of the vane, to communicate with both sides of the vane, and leading into a radially extending passage 202 extending outwardly to the radially outer extremity of the vane.

FIGS. 9, 10, and 11 represent fragmentarily a variational form of the invention, which may be considered as identical with the arrangement of FIGS. 1 through 8 except as to the construction of the clutching mechanism for operatively connecting the rotor of the vane type motor to the central pipe section of the spinner device. FIG. 9 shows this changed mechanism in a view very similar to the FIG. 7 showing of the first arrangement. In FIG. 9, the central pipe section of the spinner is designated 27' (corresponding to section 27 of FIGS. 4 and 7), and contains a passage 28 (corresponding to passage 28 of the first form of the invention) through which drilling fluid flows downwardly under pressure during a drilling operation. The rotor of the vane type motor is shown fragmentarily at 37, with the outer housing being designated 36', and more particularly with the housing having a lower wall section 43' and an upper wall section 44' corresponding to sections 43 and 44 of FIG. 4. The bearings 69', 70', 84, and 85 serve the same function as in the first form of the invention.

Instead of the two clutching levers 129, the apparatus of FIGS. 9 to 11 includes a clutching ring which is annular about pipe section 27 and about axis 12 of the apparatus. This ring is constructed to function as a vertically movable piston, and for that purpose has a lower enlarged diameter annular portion 161 having an internal cylindrical surface slidably engaging a corresponding external 'cylindrical surface on pipe 27' at 162. Above its portion 161, ring 160 has a reduced diameter portion having a cylindrical internal surface slidably engaging a reduced diameter external cylindrical. surface on pipe sections 27 at 163, to form an annular pressure fluid chamber 164 between the ring and pipe section 27' to which the pressure of the pump of the drilling fluid within passage 28' is communicated through a passage or opening 165 in the side wall of pipe 27'. The ring is retained against rotation relative to pipe 27 while permitting axial movement of the ring, by one or more keys or splines 166, which may be secured in fixed position within grooves or recesses in pipe 2.7, and be slidably received within opposed axially elongated and axially extending grooves 167 formed in the inner surface of the upper portion of ring 160. The ring is yieldingly urged downwardly by a number of evenly circularly spaced coil springs 168, which may be partially received within opposed recesses in an upper retaining ring 169 and the upper surface of movable ring 160. Retaining ring 169 may be located against upward movement by engagement against the inner race of roller bearing 69'.

Externally, the ring or piston 160 has a series of evenly circularly spaced clutch teeth or lugs 170 projecting radially outwardly to a position in which they can mesh with inwardly projecting evenly circularly spaced lugs 171 carried by and formed in rotor 37'. These teeth are movable out of their driving interfitting engagement by upward movement of ring 160 from the FIG. 9 position to the FIG. 10 position.

When super-atmospheric pressure is applied to drilling fluid or mud within the interior of passage 28', that pressure is communicated through passage 165 to the underside of the annular piston or ring 160, to actuate that piston upwardly to its FIG. position, in which it cannot transmit rotation between pipe 27 and rotor 27', to thus enable free rotation of the entire drill string and pipe section 27' without corresponding rotation of the rotor. When the drilling fluid pressure is reduced, preparatory to an operation in which the spinner may be used, the ring 160 is moved downwardly to its FIG. 9 position by springs 168, to engage teeth 170 and 171 in a manner enabling rotor 37' to turn pipe section 27 and the connected kelly or other pipe section therebeneath, to make or break a joint in the string. The operation of the remainder of the apparatus is the same in FIGS. 9 through 11 as in the other form of the invention.

What is claimed is:

1. A spinner for driving a well pipe through which drilling fluid flows into the well, said spinner comprising an element to be connected to and turn said pipe, powered drive means for turning said element and through it turning said well pipe, said drive means being actuable between an active condition in which it can drive the pipe and an inactive condition in which it can not drive the pipe, and automatic control means operable to automatically actuate said drive means from said active condition to said inactive condition in response to an increase in said drilling fluid pressure.

2. A spinner as recited in claim 1, in which said ele ment is a tubular element connectible to said well pipe and through which said drilling fluid passes.

3.- A spinner as recited in claim 1, in which said element is a tubular element connectible to said well pipe and through which said drilling fluid passes, said control means including means carried by said tubular element and subjected to and responsive to variations in the pressure of drilling fluid therein.

4. A spinner as recited in claim 3, including threads on the lower end of said tubular element for connection to said drill pipe, and threads on the upper end of said element for connection to the rotary stem of a well swivel.

5. A spinner as recited in claim 1, in which said element is a tubular element connectible at its lower end to said pipe and at its upper end to a swivel and containing a passage through which said drilling fluid flows during drilling, said element having an opening in its wall, and said control means including pressure responsive means subjected to the pressure of drilling fluid in said passage through said opening. 6. A spinner as recited in claim 1, in which said drive means include motor means and clutch means for releasably coupling said motor motor means to said element, said control means being operable in response to said increase in drilling fluid pressure to actuate said clutch means to uncoupled the motor means and said element.

7. A spinner as recited in claim 1, in which said element is a tubular element connectible at its lower end to said pipe and at its upper end to a swivel and containing a passage through which said drilling fluid flows during drilling, and said drive means including a motor having a rotor disposed about said tubular element, and a clutch operable to -releasable couple said rotor to said element for rotation in unison therewith about the axis of said element, said control means including means subjected to the pressure of fluid within said passage for actuating the clutch in accordance with changes in said pressure.

8. A spinner as recited in claim 7, in which said clutch means include a lever connected pivotally to said tubular element for swinging movement between driving and released conditions, and means forming a shoulder turning with said rotor and engageable with said lever only in said driving position thereof to transmit rotary motion from the rotor to said element.

9. Aspinner as recited in claim 1, in which said element is a tubular element connectible at its lower end to said pipe and at its upper end to a swivel and containing a passage through which said drilling fluid flows during drilling, said element having an opening in its wall, and said control means including a piston in said opening and subjected to the pressure of drilling fluid in said passage and responsive thereto to actuate said drive means between said conditions, said piston being sealed with respect to said opening to prevent fluid flow therethrough. 10. A spinner as recited in claim 1, in which said element is a tubular element connectible at its lower end to said pipe and at its upper end to a swivel and containing a passage through which said drilling fluid flows during drilling, said element having an opening in its wall, and said control means including pressure responsive means subjected to the pressure of drilling fluid in said passage through said opening, said opening being sealed against flow of said drilling fluid therethrough.

11. A spinner as recited in claim 1, in which said element is a tubular element connectible at its lower end to said pipe and at its upper end to a swivel and containing a passage through which said drilling fluid flows during drilling, said drive means including a motor having a rotor disposed about said tubular element, and a clutch operable to releasably couple said rotor to said element for rotation in unison therewith about the axis of said element, said control means including an essentially annular piston disposed about said element and movable axially by the pressure of fluid in said element and operable by said axial movement to actuate said clutch.

12. A spinner for driving a well pipe through which drilling fluid flows into the well, said spinner comprising an element to be connected to and turn said pipe, powered drive means for turning said element and through it turning said well pipe, said drive means being actuable between an active condition in which is can drive the pipe and an inactive condition in which it can not drive the pipe, and automatic control means operable to automatically actuate said drive means from said active con dition to said inactive condition in response to an increase in said drilling fluid pressure and operable to automatically return said drive means to said active condition in response to a decrease in said drilling fluid pressure.

13. A spinner for driving a well pipe through which drilling fluid flows into the well, said spinner comprising an element to be connected to and turn said pipe, powered drive means for turning said element and through it turning said well pipe, said drive means including motor means and clutch means for releasably coupling said motor means to said element, said clutch means being actuable between a coupled condition in which said motor means can drive the pipe and an uncoupled condition in which said motor means can not drive the pipe, and automatic control means operable in response to an increase in said drilling fluid pressure to automatically actuate the clutch means from coupled to uncoupled condition, and in response to a decrease in said pressure to automatically return the clutch to coupled condition.

14. A spinner for driving a well pipe through which drilling fluid flows into the well, said spinner comprising an element to be connected to and turn said pipe, powered drive means for turning said element and through it turning said well pipe, said drive means being actuable between an active condition in which it can drive the pipe and in inactive condition in which it can not drive the pipe, and automatic control means operable to automatically actuate said drive means from said inactive condition to said active condition in response to a decrease in said drilling fluid pressure.

15. For use in a well installation having a unit which is normally in a first condition dun'ng an actual drilling operation and is normally in a second condition when a threaded joint in the well pipe is being connected or disconnected; the combination comprising a power operated spinner for turning an upper section of said pipe to make or break a threaded joint, said spinner being actuable between an active condition in which it can drive the pipe and an inactive condition in which it can not 13 drive the pipe, and automatic control means operable to automatically actuate said spinner 'from said active condition thereof to said inactive condition in response to a predetermined change of said unit from said second condition thereof to said first condition thereof for drill- 16. A combination as recited in claim 15, in which said spinner'includes a clutch which acts in said active condition to transmit driving force from the spinner to said upper section of the well pipe and which in said inactive condition is released and will not transmit driving force to the Well pipe, said automatic control means being operable to actuate said clutch automatically in response to said predetermined change in condition of said unit.

17. A combination :as recited in claim 15, in which said automatic control means are operable to return said spinner from said inactive condition thereof to said active condition in response to change of said unit from said first condition thereof to said second condition.

1 8. For use in a well installation having a unit which is normally in a first condition during an actual drilling operation and is normally in a second condition when a threaded joint in the well pipe is being connected or disconnected; the combination comprising a power operated spinner for turning an upper section of said pipe to make or break a threaded joint, said spinner being actuable between an active condition in which it can drive the pipe and inactive condition in which it can not drive the pipe, and automatic control means operable to automatically actuate said spinner from said inactive condition thereof to said active condition in response to a predetermined change of said unit from said first condition thereof to said second condition.

19. A device for driving a well pipe, comprising a tubular element connectible at its lower end to said pipe and containing a passage through which drilling fluid passes, a vane type fluid motor for driving said element and including a housing disposed about said tubular element and a rotor in the housing disposed about said element and adapted to be driven about the axis of the element by the pressure of an actuating fluid, means for retaining said housing against rotation, clutch means interposed radially between said element and said motor actuable between an active condition for coupling the rotor to said element in rotary driving relation and an inactive condition enabling rotation of said element without the rotor, and means for automatically actuating said clutch means between one of said conditions thereof and its other condition in response to a change in pressure in said drilling fluid passage within said element.

20. A device as recited in claim 19, in which said clutch means include at least one lever pivotally connected to said element at a location within the rotor, and a shoulder on the rotor engageable in driving relation with said lever in one position thereof but not in a second position, there being an opening in the wall of said tubular element, said last mentioned means of claim 19 including a sealed piston in said opening exposed to the pressure of drilling fluid in said passage in said element and actuable upon an increase in said pressure to actuate said lever to said second position.

21. A device as recited in claim 19, in which said last mentioned means include a generally annular piston disposed about said element and within said rotor and movable axially relative to said element but keyed against relative rotation, said clutch means including a shoulder on said piston engagable in driving relation with a shoulder on the rotor in one position of the piston but releaseable therefrom in a second position, and an opening in the wall of said element placing said piston in communication with said passage in said element in a relation to actuate said piston to said second position in response to an increase in the pressure of drilling fluid in said passage.

22. A device for driving a well pipe through which drilling fluid flows into the well, said device comprising an element to be connected to and turn said pipe, powered drive means for turning said element and through it turning said well pipe, said drive means including a motor and being actuable'between an active condition in which the motor can drive the pipe in a predetermined rotary direction and an inactive condition in which the motor can not drive the pipe in said predetermined rotary direction, and automatic control means operable to automatically actuate said drive means from one of said conditions to the other in response to a change in the pressure of said drilling fluid.

23. A device for driving a well pipe through which drillingfluid flows into the well, said device comprising an element to be connected to and turn said pipe, powered drive means for turning said element in either rotary direction and through it turning said well pipe, said drive means being actuable between an active condition in which it can drive the pipe and an inactive condition in which it can not drive the pipe in either of said rotary directions, and automatic control means operable to automatically actuate said drive means from one of said conditions to the other in response to a change in the pressure of said drilling fluid.

'24-. A device as recited in claim 22, in which said element is generally tubular and contains a main passage through which said drilling fluid flows downwardly, said control means including a pressure sensing plunger which is movable within a small second passage formed in the side wall of the tubular element, said plunger extending to a location near the juncture of said second passage with said first passage to block substantial flow of drilling fluid into said second passage.

References Cited UNITED STATES PATENTS 2,317,306 4/ 1943 Smith 173-57 2,863,638 12/1958 Thornburg 173-57 3,282,339 ll/ 1966 Hasha l170 X ERNEST R. PURSER, Primary Examiner US. Cl. X.-R. 

